Governor



June 30, 1925. 1,544,238

r A. "r. KASLEY GOVERNOR Filaaan. 5. 1925 a Sheets SH e'et 1 ATTORNEYJune 30, 1925. 1,544,238

A. T. KASLEY Y GOVERNOR Filed Jan. 5, 1925 3 Sheets-Shee't 2 1% A'TJWIW()VV VI ESSESZ I ww- ATTORNEY June 30, 1925.

A. T. KASLEY GOVERNOR Filed Jan. 5. 1925 3 sheets sheet 5 WyN ESSE?ATTORN EY Patented June 30, 192 5.

UNITED STATES ALEXANDER T. KASLEY, OF ESSINGTON,

HOUSE ELECTRIC AND MANUFACTURING COMPANY,

SYLVANIA- PATENT 0mm.-

PENNSYLVANIA, ASSIGNOR' TO WESTING- A CORPORATION OF PENN- GOVERNOR.

Application filed January 3, 1923. Serial No. 610,514.

To all whom it may] concern:

Be known that I, ALEXANDER T. KASLEY, a citizen of the United States,and a resident of Essington, in the county of Delaware and State ofPennsylvania, have invented a new and useful Improvement in Governors,of which the following is a specification.

My invention relates to governing mechanism, more particularly of thefluid pressure type, and it has for its object to provide apparatus ofthe characterdesignated which shall be economical to build and tooperate,

which shall be reliable and stable in operation, and which shall becapable of maintaining closely regulated speeds for different loadsimposed upon a machine with which the governing mechanism is associated.

Another object of my invention is to provide fluid-pressure actuatedgovernor mechanism which shall be capable of interrupting the supply ofenergy to a machine should the supply of pressure fluid to the governingmechanism fail or should parts of the governing apparatus break.

A further objectof my invention is to provide a fluid-pressure governingmechanism whose exhaust is utilized for the purpose of lubricating anysuitable parts or bearlngs.

Apparatus made in accordance with my invention is illustrated in theaccompanying drawings, forming apart of this application, in which Fig.1 is a side elevation of a turbine showing my improved'governingapparatus applied thereto; Fig. 2 is a diagrammatic and sectional viewof the governing apparatus shown in Fig. 1; Fig. 3 is a sectional detailview on a larger scale of a constant:pressure valve shown in Figs. 1 and2; Fig. 4 is a detail view showing how the housing for thespeed-responsive mechanism is supported; and Fig. 5 is a diagrammaticview of distant-control mechanism.

Referring now to the accompanying drawings' for an understanding of myinvention, I show a motor or prime mover, at 10, for example, a steamturbine, having an energycontrolling device or admission valve, at 11,

A the valve being moved in opening and closing directions in accordancewith the load by means of fluid-pressure governing'mechanism which isoperated by the shaft 12 of the prime mover.

The fluid-pressure governing mechanism comprises a pump '13 whichdelivers fluid under .presure to a. motor device, at 14, the latterbeing connected to the energy-controlling device or admission valve, at11, and a speed-responsive, pressure-relieving mechanism, at 15, beingprovided in order to secure operation of the apparatus in a manner to bedescribed. 7

The pump 13 may be of any suitable type. and it is driven bymeans of ashaft 16 which is geared to the prime-mover shaft 12 by means ofany'suitable gearing, at'17.

See Fig. 4. The pump receives flu1d from the storage reservoir 18 anddelivers it under pressure through the passageway 19 to the motordevice, at 14. In order that the pressure of fluid delivered to themotor device, at 14, may be constant, a ressure-regulating valve 20 isassociated wit a passageway 21, communicating with the passageway 19, asmay be seen from Fig. 3, the pressure-regulating valve 20 serving tolimit the maximum attainable pressure of fluid in the passageway 19.Therefore, the pump ,is

capable of delivering fluid at a substantially the spring or biasingmeans'29 serves to impart closing movement to the valve 11 so that,should the pressure of fluid fail, closure of the valve 11 is assured.The motor device includes suitable valve ineehani'sm-for controlling theadmission and exhaust of fluid to the cylinder or chamber 23, wherebyactuated.

The valve mechanism for the operating cylinder'comprises a valve chamber30, arranged in the head 31 for the operating cylinder 23. The head31'is provided with a chamber or passage 32, which communicates with thepressure-supply passageway 19 and with the valve chamber 30. An exhaustpassage or chamber 33 is provided in the head aggerated manner in Fig. 2for purposes of 31- and it communicates with the valve chamber 30. Asupply passage 34 communicates with the operating cylinder 23 and it isprovided witha portion 35 which communicates with the valve chamber, thelatter portion communicating with. the valve chamber 30 between theconnections of the pressure-supply and exhaust chamber or passages 32and 33 therewith.

A valve 36, preferably of the piston type,

fits in the valve chamber 30 and it is provided with a piston valveportion 37 whose length is substantially equal to that of the passage35. The piston valve is provided with reduced portions 38 and 39, aboveand below the piston portion 37. As the piston portion 37 has 'anedgefit with the sides of the passage 35, when the valve is in its neutralposition, it will be apparent that movement of the valve upwardly fromthis position laces the pressure-supply passage or cham er 32 incommunication with the operating cylinder 23 and that downward movementof the valve places the exhaust chamber or passage 33 in communicationwiththe operating cylinder. The piston valve 36 is preferably arrangedcoaxial with respect to the rod 25and it has a close clearance 41 withrespect thereto for a purpose to be described.

When the piston valve 36 moves upwardly in response to an increase inload on the prime mover, the pressure-supply passage or chamber 32 isplaced in communication with the operating cylinder 23, whereupon theoperating piston 24 is moved downwardly to open the valve 11 wider toadmit an increased quantity of motive fluid to the prime mover in orderto take care of the increased load. This downward movement of theoperating piston 24 is accomplished by a compression of the spring 29,whose eflect will be more fully hereinafter set forth. \Vith a decreaseof load on the prime. mover the piston valve 36 moves downwardly toplace-the operating cylinder in communication with the exhaust by way ofthe passages 34 and 35, the reduced portion 38, and the exhaust chamberor passage The operating mechanism for the piston valve 36-to secure theupward and downward -movements thereof referred to comprises a piston,element, or abutment 42 connected to the piston valve 36 and arrangedwithin a cylinder or chamber 43. The piston has a stem 44 on theopposite side from the piston valve and the piston and stem structurehave a close sliding fit with respect to the rod 25. As .shown, the stem44 extends through the head 45 of the cylinder 43 and it abuts the lowerend of the spring 29, the latter being normally held under compressionbetween the stem and an abutment 46, such as a nut, on the rod 25.

The clearance space 41 (shown in an exclearness) between the rod 25 andthe interior of the piston valve 30 constitutes an orifice connectionfor the space of the cylinder '43 beneath the piston 42, this orificeconnection including ports 47, whch afford and itwill be seen that itsforce opposes the fluid pressure forces applied to the operating piston24 and to the piston 42.

The piston 42 is moved downwardly due to the force of the spring 29 andit is moved upwardly due to flu'id pressure effective beneath the piston42 whenever the effective force of such pressure exceeds that of thespring. When the piston 42 occupies such a position that the pistonportion 37 of .the piston valve 36 is in a neutral position, then thepiston 42 is in an'equilibrium position, that is, the force of thespring 29 acting above is counteracted by an opposed and equal effectivefluid pressure force applied beneath the piston 43 and beneath thepiston portion 49 of-the piston valve. In order thatthe fluid pressurebeneath the piston 42 may be maintained substantially conprises apassageway 50 which is connected to the speed-responsive,pressure-relieving mechanism. at 15. The speed-responsive,pressure-relieving mechanism tends to restrict the discharge of fluidwhenever the speed of the turbine drops slightly due to an increase inload, with the'resultthat pressure beneath the piston 42 builds up tomove the piston valve 36 upwardly in order that fluid under pressure maypass from the chamber or passage 32 by Way of the reduced portion 39 andthe passages 35 and 34 to the operating cylinder 23 for the purose ofmoving the piston 24 downwardly in order to open widerthe-energy-controlling device or admission alve 11 to admit an increasedquantity of'motive fluid to the prime mover. This downward movement ofof the operating the piston 24 continues until the tension ofthe spring29 is substantially equal to the effective fluid-pressure force actingbeneath the piston 42 and the piston face 49 at which JllIlO the pistonvalve ,36 occupies a ncutra or cut-off position.

With an increase in speed of the prime mover, incident to a decrease inload, pressure beneath the piston 42 is relieved, with the result thatthe piston is forced downwardly by the spring 29, thereby connecting theoperating cylinder 23 with the exhaust chamber or passage 33 by way ofthe passages 34 and 35 and the reduced portion 38 of the piston valve,whereupon the spring 29 is then effective to move the operating piston24 upwardly. This upward movement of the operating piston '24 and itsrod 25 results in movement of the valve 11 in a closing direction. Theupward movement piston 24 is accompanied by a diminution in the force orcompression of the spring 29; and, when the compression of the spring 29is reduced so that the force thereof is substantially equal to the forceof the fluid pressure effective beneath the piston 42, then the lattermoves to equilibrium position with the piston valve 36 in a neutral orcut-off position.

It will, therefore, be seen that any change in load upon the prime moveris accompanied by a disturbance of the condition of equilibriun'i of theforces acting on the piston valve structure, with the result that theoperating piston 24 is moved to secure movement of the admissionva-lve11 in the proper direction, this movement of the operating pistoncontinuing until equilibrium of forces acting thereon is restored atwhich time the piston valve 36 occupies a neutral or cut-off position.

The speed responsive relief or bleeder apparatus comprises a hollowshaft 51, which is secured to the upper end of the pump shaft 16, andwhich communicates with the passageway by means of ports 52,communicating with an annular cham ber 53, the latter being connected tothe passageway 50. The hollow shaft carries a suitable head 54 at itsupper end, this head being provided with a bottom 55 and a part-ition56-spaced above the bottom, the partition defining, with the bottom, anexhaust receiving chamber 57. The partition 56 and. the bottom 55 areprovided with openings to receive the valve cylinder 58- which isaxially alined with the hollow passage 59 of the shaft 51. The cylinder58 is provided with ports 60 which are covered and uncovered inoperation by means of a piston 61.

move thepiston 61 upwardly to open the ports 60. A spring 66 isconnected to the arm 64 and to-the head 54 and its force opposes thecentrifugal effect of the weight 65 and it tends to move the piston 61downavardly to close the ports 60. In addition to the opposing forcesjust mentioned, acting on the piston valve 61, the force of the fluidbeneath the piston 61 is also effective in determining the positionthereof. In operation, whenever the piston 61 occupies a given position,the force of the fluid effective beneath the piston 61 added to thecentrifugal force effective on the weight 65 equals the force of thespring 66.

Theconnection of the spring 66 with the arm 64 is of the adjustable typeso-that the tension of the spring 66 maybe varied for the. purposeof'changing the normal speed of the prime mover. As shown, thisadjustable connection consists of a threaded anchor member- 67 -for'oneend of the spring 66 which has threaded engagement with a screw 68carried by the arm 64. Thetension of the spring 66 may be varied merelyby turning the screw 68 in one direction or the other.

Thoexhaust chamber 57 communicates with a collection chamber 69 by meansof ports 70. The collection chamber is formed by a part of thestationary structure which includes the chamber 53; and, beyond thecollection chamber 69, such stationary structure extends outwardly asindicated at 71 to constitute the bottom of the housing 72 for therotary head 54. A drain 71' is shown in the bottom structure 71. Theexhaust passage orch'amber 33 in the head 31 is con nected to anexhaustpassageway 73 which leads to bearingsindicated at 74 requiringlubrication. If desired, the space beneath the piston 24 may beconnected to the passageway 73 by means of a suitable passageway 75.Also, if desired, the passageway leading from the constant pressurevalve 29 pressure passage or chamber 32 of the-opcrating cylinder head31, such pressure be ing maintained substantially constant due to theemployment of a constant pressure valve 20. Fluid under pressure fiowsfrom the pressure chamber or passage 32 to the space inthe cylinder 43beneath the piston 42 by way of the orifice connection constitutedby thehole 47 clearance space 41 between the piston valve 36 and the rod 25.

The spring 29 under initial compression movement in a closing directionto the valve A For normal operation of the prime mover at a given load,the piston valve 36 occupies a neutral or cut-off positiom'the piston 42being maintained in an equilibrium posi tion, .the force of the spring29 thereon being balanced by the fluid pressure force effective beneaththe piston 42 and beneath the face 49.

Since fluid is being supplied to the space beneath the piston throughthe orifice connection, it is necessary, for agiven speed, that fluidshall be -bled from the cylinder 43 beneath the piston 42. Therefore,for all speeds, there is more or less bleeding of fluid through thepassageway 50, the passageway 59, and the ports 60, the restriction ofthe latter being under the control of the piston valve 61.

For a given speed and load, the piston 42 is maintained in equilibriumposition by an oil pressure acting therebelow, which, in turn, ismaintained substantially constant by the valve 61 cooperating with theports 60, that is, the valve 61 occupies a given position which dependsupon the force of the oil pressure acting beneath the piston 61, uponthe centrifugal force effective on the (pgeight 65 and upon the tensionof the spring If the'load on the prime mover should increase, the speedthereof would drop slightly with the result that the centrifugal forceof the weight member 65 would decrease, thereby disturbing theequilibrium condition-of the forces acting on the piston 61 andpermitting the spring to move the piston 61 ggwnward to restrict thepassages or ports Therestriction of bleeding from the cylinder 43results in thebuilding up of pressure beneath the piston 42 and, thefluid pressure exceeding the force of the spring 29, the piston 42 movesupwardly to establish communication between the pressure supply chamberor passage 32 and the oper-. atmg cylinder 23 so that fluid underpressuremay act on the piston 24 to move the admission valve in anopening direction to supply an increased quantity of motive fluigl tothe prime mover to meet the increased load.

Whenever there is a decrease in load, resultlng in a decrease in fluidpressure beneath the piston 42, the piston valve moves downwardly toconnect the operating cylinderwith the exhaust, whereupon the spring 29is effective to pull the piston 24 upwardly to move the admission valve11 in a closing direction to restrict the flow of motive fluid to theprime mover. This upward movement of the operating piston continuesuntil the force of the spring 29 is diminished sufficiently so thatthepiston 42 can return to neutral position.

If the pressure of fluid for the governing mechanism should fail, thepressure of the spring 29 would immediately exceed the pressure of fluidbeneath the "piston 42, whereupon the latter would move downwardly toplace the operating cylinder 23 in communication with the exhaustchamber or passage with the result that the operating piston 24 and therod 25 would move upwardly and the admission valve 11 would move in aclosing direction due to the forceof the spring 29. If the spring 66 ofthe speed-responsive device should fail, then the piston valve 61 wouldbe free to move to expose to a greater extent the ports under theinfluence of the weight and the pres sure of fluid effective beneath thepiston. valve 61. The sudden reduction of fluid pressure beneath thepiston 42 in this way results in the downward movement of the latter andthe movement of the admission valve in a closing direction under the in-I fluence of the spring 29 in the manner just staged.

In operation there is more orless leakage beneath the piston 42 in orderthat the latter may acquire an equilibrium position. The greater theback pressure the less the Speed. of theiprime mover for the reason thatit is necessary that the piston valve 61 restrict the bleeding of fluidfrom beneath the piston 43 to an extent suflicient to obtain anequilibrium condition of this piston. Accordingly, therefore, I show apressure regulating valve associated with the head 45 for regulating theback pressure in the cylinder 43 and'above the piston 42.

The. pressure-regulating valve comprises a valve member 76 whichcooperates witha seat provided at one end of the outlet passage 77. Aspring 78 abuts against oneend ofthe valve member and the other end ofthe spring abuts against an adjustable member 79, which may be adjustedfor the purpose of varying the compression of the spring 78, whereby thepressure of fluid necessary to raise the valve member 76 may 1,544,288valve member preferably enters a. chamber The operation of speedchanging just re- 80 which communicates with a suitable ferred to isparticularly advantageous when drain 81. synchronizing one machine withanother.

If the compression of the spring 78 is This operation may beconveniently carried lessened, the speed of the prime mover tends outfrom a distance, as will be apparent to increase for the reason that theback presfrom Fig. 5. In this view, I show a lever sure above the piston42 is, less and conse- 82 arranged between the screw 79.,and the quentlythe fluid pressurebeneath the piston spring 78, the lever beingfulcrumed at 83 I 42 to hold the latter in neutral or equilibriandhaving its other end pivotally connected move upwardly so as to supplyfluid under when the back pressure is decreased, the pispressure springmay be readily um position is less, the diminished pressure at 84 with arod or link 85, which'is conbeneath the piston 42 being obtained by anected to the diaphragm of a pressure desliightly greater opening of theports 60 vice'86. One side of the diaphragm, is subwhich takes place dueto upward movement ject to atmospheric pressure while the other of thepiston valve 61 incident to an increase side is subject to asub-atmospheric presin speed of the turbine. sure, which may be varied,whereby the The first effect of decreasing the back compresion of thespring 78 may be varied pressure on the piston 42 is for the latter toat will.

The sub-atmospheric side of the regulatpressure to the operating piston24 to move ing device 86 is connected by means of a the latterdownwardly and to open wider passageway 87 with the throat of an ejectorthe admission valve 11, whereby more mo- 01' aspirator 88, the latterpreferably utiliztive fluid is admitted to the'prime mover to ing waterat constant pressure which is dissecure the increase in speedalready'referred charged axially of the ejector or aspirator to for thepurpose of bleeding the pressure by means of a suitable passageway.89.If beneath the piston 42 in order that the latwater is used as themotive fluid of the ter may attain a position of equilibrium. ejector oraspirator, this water may be con- An increase in compression of thespring veniently supplied from the turbine gland 78, results in adiminution in the speed of, supply. In order that the pressure devicethe prime mover for the reason that as soon 86 may have thesubatmospheric pressure as the back pressure is increased in this way,varied, I provide means for bleeding air the piston 43 moves downwardlyto place from the atmosphere into the passageway 87. the operatingcylinder 23 in communication The air bleeding arrangement preferablywith the exhaust, whereupon the spring 29 comprises valve mechanism at90'which may is effective to move the operating piston 24 he supportedby a switch board 91 of a and rod 25 upwardly to move the admissionpower plant. The valve mechanism controls valve 11 in a closingdirection, this movethe admission of air from the atmosphere mentcontinuing until the fluid pressure efthrough the passageway 92 to thepassagefective beneath the piston 42 is equal to the way 87, This valvemechanism preferably opposed back pressure and the pressure 04 comprisesa suction operated valve member the spring 29. As soon as the flow Of 110- 93 which is biased toward its seat by means tive fluid to the primemover is restricted, of a spring 94 connected to the valve and its speeddrops, with the result that the to a tension adjusting member 95. Ascentrifugal force of the welght member 65 shown, the tension adjustingmember 95 is a declines and the spring member 66contractsimpl l verfulcrumed at 96 and having a until the speed-responsive device attains al in djust ent 97 with respect to a, condition of equilibrium. Thisoperation of s ctor 98. -As the tension of the spring 94 thespeed-responsive device results in the is increased bleeding of thepassageway 87 restriction of bleeding from b ne h the is diminished withthe result that the subpiston 42, whereby the fluid pressure,heatmospheric pressure is increased and the neath this'piston' buildsup. tension of the spring 78 is'diminished. If

It Will, therefore, be Seen that a equi the tension of the spring 94 isdiminished,

rium or neutral p siti n 0f he pist n 2 the sub-atmospheric pressure inthepassageis attained, when the bagk P1?Ssure is way 87 is increasedwith the result that the creased, bOiLh by a decrease in the COIIIPIES-rod 85 moves upwardly and the tension of sion of the spring 29 nd by nflfl the spring 78 is increased. Itwill, therethe fluid pressure beneaththe piston 42 111- fore, be apparent that, with the apparatus cident toa restriction in the bleeding; and, h wn i 5, the tension 'of the backcontrolled ton 42 attains a position of equilibrium both from adistance. 1 by a decrease in the compression of the A clpser degreeof'regulat on may be obspring 29 and a decrease in the'pressure betainedby the use pf a spring 29 of finer neath the piston 42, the latterdecreased scale; however, as this spring is weakened,.

pressure being obtained by anincreased' cathe stability of the'mechanismis decreased. pacity for bleeding incident to an increase in speed ofthe prime mover. speed variation from no load -to full load With astronger spring, the percentage in i may be greater, but the stabilityof the 6 For example, if the tension of the spring 66 is' increased,this means that the piston valve member 61 is moved inwardly to restrictthe ports 60 which, as already stated, results in the building upofpressure beneath the piston 42 and the consequent opening of theadmission valve 11 to a wider position. This results in an increase inthe speed of the prime mover or turbine, and

the speed-responsive mechanism attains a condition ofequilibrium wherethe spring 66 and-the centrifugal force of the weight member 65 and theeffect of the oil pressure on the piston 61 are balanced, with'a greaterrestriction of the ports 60. An increase in tension of the spring 66,therefore, results in a higher speed for the prime mover. A decrease intension of this spring results in a contrary effect.

M improved governing mechanism preferab ggu'ses lubricating oil as anactuating fluid. I, therefore, show the outlet passageway 73 for thedischarge chamber 33, the outlet passageway 7 5 for the space beneaththe operating piston 24, the discharge conduit 103 for the dischargechamber 69, and

"the pressure-relief valve 20 for the pressure.- supply conduit 19, allcommunicating with the conduit 100, which is provided with connections101 leading to the bearings 7 4 for the purpose of lubricating thelatter. Surplus oil from the bearings is discharged into a passageway orconduit 102, which comnnunicates with the receiver or reservoir 18. Itwill, therefore, b seen that I have provided a combined governing andlubricating system in which oil issupplied at sufficient pressure fromparts of the governing mechanism to secure adequate lubrication.

When starting up the prime mover, it is necessary to supply fluid tothepassageway- 19 "from some auxiliary source. Accordingly, I show, apassageway 105 adapted to be connected to any suitable source of fluidunder pressure and which is controlled by means of a valve 106. Instarting, fluid under pressure from the auxiliary source is admitted tothe passageway 19, whereupon .such fluid enters the pressure chamber orpassage 32 and then passes through the. restricted orifice connection41, moving the piston 42 upwardly so that such fluid under pressure maybe supplied to the operating piston 24 in order to move the latterdownwardly for the purpose of opening'the admission valve 11. a Theprime mover then starts, and thereafter the auxiliary source of fluidunder pressure may be cut off and the pressure developed by the pump 13solely relied upon.

It will be obvious to those skilled in that art that the fluid-pressureoperated mechanism for the prime mover valve as well as thefluid-pressure controlling mechanism for the operated mechanism may beof any suitable type, or design, although the preferable type is thecylinder and piston kind. Also, while a spring is shown for closing theadmission valve, it is to be understood that any device capable ofproducing the same result may be used.

While I have shown my invention in but two forms, it will be obvious tothose skilled in the art that'it is not so limited, but is susceptibleof various other changes and modifications without departing from thespirit thereof, and l desire, therefore, that only such limitationsshall be placed there upon as are imposed by the prior art or asappended are specifically set forth in the claims.

. What I claim. is:

1. The combination witha prime mover having an admission valve, ofgoverning mechanism for controlling the speed of the prime movercomprising a movable preslOU 2. In governing mechanism for controllingthe supply of energy to a machine, the combination of energy-controllingmechanism including an element movable by fluid under pressure, a sourceof fluid under pressure, means for supplying fluid to said element fromsaid source and for exhausting fluid from said element, amovable elementconnected to the last-named means, means for supplying fluid at'a loweraverage pres sure to one side of the last-named element, biasing meanscooperating with said last named element to oppose movement thereof inresponse to fluid pressure, and means for relieving the pressure offluid applied to said last-named element.

3. In governing mechanism for controllin'g the supply of energy to amachine, the combination. of energy-controlling mechanism includinganelement movable byfluid under ressure in one direction, spring means formoving said mechanism, in the otherdirection, a source of fluidunder'pressure, means for supplying fluid to said element from saidsource and for exhausting fluid from said element, a movable elementconnected to the last-named means, means for supplying fluid from saidsource at a lower average pressure to one side of the last-namedelement, biasing means cooperating with said last-named means and saidelement to oppose the fluid pressures, and means for relieving thepressure of ,fluid applied to said last-named element.

4. In governing mechanism for controlling the supply of energy to amachine, the

combination of energy-controlling mecha-' nism including an elementmovable in one direction by a fluid under pressure, a source of fluidunder pressure, means for supplying fluid to said element from saidsource and for exhausting fluid from said element,

a movable element connected to the last named means, an orificeconnection for sup- 7 plying, fluid from said source to one side of thelast-named element, spring means cooperating with said moving elementsand exerting its force thereupon in opposition to the fluid pressuresapplied thereto, and means for relieving the pressure of fluid appliedto said last-named movable element in accordance with the speed'of themachine.

5. The combination with a steam motor having an admission valve, ofgoverning mechanism for the motor comprising a movable abutmentconnected to the valve, a source of fluid under pressure, a valve forcontrolling the admission of fluid from said source to one side of the.abutment and the exhaust of such fluid therefrom, an abutment connectedto the valve, a restricted orifice connection for supplying fluid to oneside of the latter abutment from said source, speed-responsive means forrelieving the fluid pressure on the latter abutment, and biasing meansto secure movements of the abutments in directions opposite to movementsthereof in response to fluid pressure whenever the force of the biasingmeans exceeds that of the fluid pressure.

6. The combination with a motor having an admission valve, of governingmechanism' for the motor comprising a movable abutment connected to thevalve, a source of fluid under pressure, a valve for controlling theadmission of fluid'from said source to the abutment and for controllingthe exhaust of fluid therefrom, a movable abutment carried by the valveand normally subject to a pressure less than that of said source,speedresponsive means for relieving the pressure applied to the latterabutment, and spring means operative When the pressure on the latterabutment is relieved to move the valve to exhaust fluid from the firstabutment and then to move the admission valve toward its closingposition.

7. The combination with a motor having an admission valve, of governingmechanism for the motor comprising a spring for moving the valve in aclosing direction, an operating piston for moving the valve in anopening direction and in opposition to the spring, a source of fluidunder pressure,

a piston valve for controlling the admission of fluid from said sourcetoone side of said: piston and the exhaust of fluid therefrom, anoperating piston connected to the piston valve and subject to thepressure of said spring on one side and to the pressure of fluid on theotherside, and speed-responsive means for relieving the pressure offluid applied to the latter operating piston.

speed-responsive means for controlling the relief of fluid pressure fromsaid valve-operating piston so that the valvemay come toa neutralposition under influence of the spring. 1 Y

9. The combination with a motor having an admission valve, means fordeveloping fluid under pressure driven by said motor,

an operating piston connected to the admission valve, a valve forcontrolling the admission of fluid from said pressure-developingmeans'to one side of said operating piston and the exhaust of fluidtherefrom, an

operating piston connected to the valve,

means for supplying fluid under pressure p to one side of the latteroperating piston, a spring for exerting forces on said operating pistonsin opposition to the fluid pressure forces applied thereto, andspeed-responsive ineansfor relieving the pressure of fluid applied tothe operating piston of the valve.

10. The combination with a motor having" an admissionvalve, of.governingmechanism for the motor comprising pressure-developing means driven bysaid motor,'an operating cylinder, an operating piston in the cylinder,a rod for connecting the piston to the admission valve, a piston valvefor contro ling the admission of fluid from said pressure-developingmeans to said piston and the exhaust of fluid therefrom, a secondoperating cylinder in axial alinement with ing piston.

means, a spring under compression arranged between said rod and thesecond operating piston and exerting its force on the latter inopposition to fluid pressure, and speed-responsive means forrelievingpressure from the second operating piston.

" 11. The combination with a motor having an admission valve, ofgoverning mechanism therefor comprising fluid pressure' developing meansdriven by the motor, an operating cylinder, an operating piston arrangedwithin the cylinder, a rod for connecting the operating piston to theadmission valve, a piston valve arranged coaxial with said rod forcontrolling' the admission of fluid from said pressure-developing meansto one end of the operating cylinder and the exhaust of fluid therefrom,a second operating cylinder alined with the first cylinder, a secondoperating piston arrangedwithin the second operating cylinder andconnected to the piston valve, means for-admitting fluid under pressureto one side ofithe second operating piston through a restricted orificeconnection, a spring under compression arranged between said rod and thesecond opcrating piston and serving to oppose the fluid pressuresapplied to the pistons, and speed-responsive means for relieving thefluidpressure applied to 'the second operat- 12. The combination with amotor having an admission valve, of governing mechanism for the motorcomprising fluid-pres; sure developing means driven thereby, anoperating cylinder, an operating piston arranged within the cylinder andconnected to the admission valve, a valve for controlling the admissionof fluid from said pressure-developing means to one end of the operatingcylinder and the exhaust of fluid therefrom, a second operatingcylinder, a second operating piston arranged within the cylinder andconnectedto the valve, a restricted orifice connection between thepressure-developing means and the second operating cylinder, :1. springunder compression for exerting its force against said opera-ting pistonsin opposition to the fluid pressures 1 applied thereto, andspeed-responsive means for relieving the pressure of fluid applied tothe second operating piston.

13. The combination with a motor having an admission valve, of governingmechanism for the motor comprising pressure-developing means driven bythe motor, an operating cylinder, an operating piston ar ranged withinthe cylinder, a rod for connectingthe piston to the admissionvalve, aslide valve for controlling the admission of pressure fromfluid fromsaid fluid-pressure developing means to one end of the cylinder and thesecond operating piston, a spring under compression between the firstand second oper ating pistons for normally opposing the fluid pressure-sapplied thereto, and speedresponsive means for delivering the pressureof fluid applied to the second operating piston. I I

14; The combination with amotor having an admission. valve, of governingmechanism for 'the motor comprising fluid-pressure developingmeansdriven by the motor, an operating cylinder, an operating pistonwithin the cylinder, a piston rodfor con= necting the piston with theadmissionvalve, a piston valve surrounding the piston rod and havingslight clearance with respect thereto, a valve cylinder having passagescommunicating with said pressure-developing means and with the exhaust,means on the valve for placing the operating cylinder in communicationwith the pressure-developing means or with the exhaust dependent uponthe valve position, a second operating piston connected to the valve,ports in the valve connecting the clearance'sp'ace with respect to thepiston rod with said pressure-developing means and with the space at oneside of the second operating p1ston a spring under compression and act-4 mg on both pistons to oppose the fluid pressures applied thereto, andspeed-responsive means for relieving the pressure of fluid applied tothe second operating piston.

15. The combination with a prime mover having anadmission valve, of aspring for moving the valve in a closing direction, an

operating piston for moving the valve in an opening direction,fluid-pressure developing means driven by the prime mover, a valve forcontrolling the admission of fluid under said pressure-developing meansto one side of the piston and'the exhaust of fluid therefrom, anoperating piston connected to the valve, a restricted orifice connectionbetween the pressure-developing means and one side of the secondoperating piston, adjustable pressure-relief means associated with thespace at the other side of the second operating piston, andspeed-responsive means for relieving the pressure of fluid applied.tothe first side of said second operating piston.

16. Thecombination with a prime mover having-an admission valve, of aspring for moving the valve in a closing direction, a fluid motor devicefor moving the valve in an opening direction and in opposition to thespring, a hollow shaft driven by the prime mover, a valve for one end ofthe shaft, speed-responsive means for controlling the opening andclosure of said valve and rotating with the hollow shaft, and an exhaustconnection between the motor device and the hollow shaft, whereby uponoverspeeds of the prime mover, the rate of exhaust of fluid fromthefluid motor is increased thereby permitting movement of the 10admission valve in a closing direction due to the spring.

In testimony whereof, I have hereunto subscribed my name this 28th dayofDecember, 1922.

ALEXANDER T. KASLEY.

